Center section compressor

ABSTRACT

An improved rotary device of the angle piston type for effecting compression of a gaseous fluid characterized by a center section compressor that includes uniformly shaped members intermediate the pistons and disposed in an annular chamber defined by end seals and radially inner and outer walls that engage the shaped members in fluid tight relationship so as to effect compression of a fluid trapped between adjacent members as they move from a first location in which the annular chamber is longest to a position 180* therefrom where the chamber is at its shortest; and respective intake and discharge ports for the center section compressor. Also disclosed are specific structural details of an embodiment employed in an internal combustion engine, as well as the broad concept and other applications.

United States Patent [191 Turner [11] 3,902,468 [451 Sept. 2, 1975 [73] Assignee: Turner Research, Inc., Graham,

Tex.

[22] Filed: May 13, 1974 [21] Appl. No.: 469,216

William F. Turner, Graham, Tex.

[52] 11.8. CI 123/43 A; 91/500; 417/204; 417/206; 418/270 [51] Int. Cl. F02b 57/00; FOlb 3/00; F04b 23/10 [58] Field of Search 123/43 A, 43 AA, 71 R; 91/500; 417/204, 206; 418/270 453,894 9/1936 United Kingdom 123/43 A Primary Examiner-John J. Vrablik Attorney, Agent, or Firm-James C. Fails ABSTRACT An improved rotary device of the angle piston type for effecting compression of a gaseous fluid characterized by a center section compressor that includes uniformly shaped members intermediate the pistons and disposed in an annular chamber defined by end seals and radially inner and outer walls that engage the shaped members in fluid tight relationship so as to effect compression of a fluid trapped between adjacent members as they move from a first location in which the annular chamber is longest to a position 180 therefrom where the chamber is at its shortest; and respective intake and discharge ports for the center section compressor. Also disclosed are specific structural details of an embodiment employed in an internal combustion engine, as well as the broad concept and other applications.

6 Claims, 2 Drawing Figures PATENTED EP 2197s CARB.

5/ BD-C 57 124 .2

BACKGROUND OF THE'INVENTION 1. Field ofthe Inyention This invention rclatesto arotary device of the socalled angle piston type, atleast a portion of whicheffects compression of a gaseous fluid jn a particulanas pect, it relates to compressor seetion serving as a su-. percharging means i for internal combustion engine (ICE) of the angle piston type. M i i I I I 2. Description of the Prior Art H As delineated in my copending ,patentfapplication Ser. N 'J251,317, entitledfYee Enginefifile d may 8,

1972, nowjU S. P atfNo. 3,830,208 a wide variety of devices of the so c z illed angle piston type have been employed as: universal joints for transmitting forces, pumps, compressors, fluid-poweredfmotors andas m tary vee enginesl'lri addition tothe United S tatespatents cited therein, describing pumps,'cor npressors and fluid poweredmotor sfthe following US. Pat. Nos. are cited against that application; 2,417,253; 2,444,764;

2,511,992; 2,543,134; 3,557,761 an 3,656,408; as

well as British PatJ Nos. 2,914- and 453,894'and French Pat. Nos. 450,504 and 1,001,757. I

Despite the large number of prior r e'ferences, none of the references describe apparatus having he following desirable features not her'etoforeprovided: i

l. The apparatus 'shouldhave wide flexibility, for ex ample be useable as a 'first stage of compression, a supercharger or air intake pump' for an engine, a cooling air pump for an engine or compressor or similar applications.

2. The compressor portion of the rotary device should not require any, or'a't worstzminimal, additional moving parts above those normallyr eq uiredby the ro-' tary device itself; for'e'xamplej there should'be no compressor inlet valves an'cf'cornpressm outlet valves required for the compressor" section in" addition to those normally required for the rotary'device.

3. The compressor section should' be operable on any compressible fluid,-in'cluding combustible-admixtures when employed as a*supereharger for internal combus-' tion engine.

Accordingly, it is an object of this invention. to provide an improvement in a rotary device having one or more of the foregoing-features'not heretofore-provided. 1.

It is a specific object of this device toprovidean im* provement in a rotary device that hasr'all of the-forego-- ing features nottheretofore provided; '1 r 1.

These and othe'robjects-will become apparent. from the descriptive matter hereinafter,particularly when taken in. conjunction with the drawings, BRIEF DESCii'iPiiON o rHsfikAwinos FIG. I is a partial side .elevational view, partly in vsection, of an angle pistondevicc of one. embodiment of this inventions I 4 FIG. 2 is an'end view from theveeangleend of one cylinder block section of.th.c.;anglc piston device of FIG. 1. s

DESCRIPTION OF PREFERRED EMBODI ENTS This invention has wide flexibility and mayhbeemployed with any. anglcpiston rotary device. It will described herein with respect to a vee engine of the internal combustion type. since it wasin this applicatioir that it was developed,

Referring, .to FIG. 1, a rotary vee engine 11 is modnted ona conventional base, as described in my aboveiretferenced patent application Ser. No. 251,317. The ,respective' detailedinterconnection of elements and operation ,of'theintcrnal combustion engine 11 is explained in my copending application Ser. No. 251,317 and that descriptive matter is embodied herein by reference for details not duplicated in the brief description hereinaftenThevee engine 11 may be employed, in any configuration that will accommodate its delivery ,of power in normalusage. The power may be delivered to transmissions or any other application where conventional reciprocating internal combustion engines .have been employed. The vee engine 11 includes an outer housing 15 having right and left casings 1 7 and 19. Disposed interiorly of the housing 15 are first and second cylinder blocks, such as cylinder block 21, that are rotatable about their respective central longitudinal axes and have radially spaced parallel cylinders 23. The ,vee engine 11 also has respective first and second cylinder heads, such as cylinder head 22, that are eonnectedrespectively with the first and second cylinder blocks and rotatable therewith. Respective first and second sets of pistons, such as piston 25, are disposed in the respective cylinders 23 in the cylinder blocks. The pistons reciprocate within their cylinders as the cylinder blocks rotate, simultaneously carrying the. pistons in a generally elliptical path. The pistons maintain their same relative top-on-top position, however.

The vee engine 11 has a plurality of inlet ports. such as inlet port 27, for intake of gaseous fluid within respective cylinders atop the respective pistons therewithin at-lcast by thetime each piston has attained a predetermined, first position, such as below the intake port27. Each intake port 27 is in fluid communication with its respective cylinder and with the central intake passageway 29. The vee engine 11 has a center support I 30 that; isstationary and carries cylindrical tubular members 32 ,defining the central intake passageway 29. Fluid communication with the interior of its respective cylinder is blocked, however, when the piston 25 moves above the inlet port 27. The piston thus traps the gaseous fluid for compression thereof, as in a two-cycle IC engine. In the illustrated embodiment, the gaseous fluid will be a combustible mixture formed by a combination of an oxygen-containing fluid, such as air, and fuel, such asgasoline vapors. The combustible mixture will beformed'by the admixture of the fuel with air in a devicegsuch as carburetor (CARE) 31, FIG. 2.

The vee engine 11 also has a plurality of respective exhaust, or discharge, ports 33 for discharging fluid from within the respective cylinders 23 after compression therewithin. More specifically, in the illustrated embodiment the fluids that are discharged are combustion products, including various gases, following compressionahd combustion of the combustible mixture with in thc, cylinder. The combustion products are dischargedonly after the respective pistons 25 have reciprocated below the level of their respective discharge ports 33, in the illustrated embodiment.

The vee engine 1] also has a power delivery shaft 35 for delivering power from the rotating cylinder blocks. Obviously, the shaft 35 will serve as a power delivery means for delivering power to rotate the cylinder 35 are connected with respective torque output means, such as gears, in the illustrated vee engine ll. The gears may be connected with the respective shafts so as to rotate in unison therewith; for example; by keys and keyways or by co-engaging splines. As illustrated. the shafts are tubular for use as a central oil supply passageway in the lubrication system, described briefly hereinafter.

Also, the vee engine 11 has ignition means in the form of spark plugs 37 that fire to ignite the combustible mixture as the piston nears the position equivalent to top dead center and the respective plug 37 is moved past an ignition harness (not shown).

The vee engine 11 and the respective elements described hereinbefore with respect to the FIGS. 1 and 2 are conventional and need not be amplified in detail. Similarly. conventional are the respective accessory systems, such as the oil circulation system. the exhaust system and the cooling system that are illustrated but not described in detail. For example, the oil circulation system comprises a longitudinally extending main passageway 39 with a plurality of small tributaries 41 for distributing the oil responsive to centrifugal force developed in the rotating cylinder block. Similarly, the use of air cooling, such as afforded by the cooling blower and cooling passageway 43 need not be described in detail. It is sufficient to note that the cooling air passageway flows past the fins 45 on the cylinder block for cooling. The main thrust of this invention, however, lies in the center section compressor 47. For purposes of discussion in FIG. 1 the following descriptive matter will be directed to the cross sectional view between a central lateral plane49 and the cylinder block and cylinder head shown in cross section. The

cross sectional portion of FIG. 1 is taken along the central longitudinal plane of the vee engine 11. The center section compressor 47 comprises: a plurality of uniformly shaped members 51 rotated through an annular chamber 53., FIG. 2, defined by respective radially inner and outer walls 55 and 57; a center section intake port 59; and a center section discharge port 6 The uniformly shaped members 51 are connected with the respective pistons and at least one set of pistons disposed in one cylinder block. By uniformly shaped is meant having a shape that can be rotated through the annular chamber 53 and having uniform lateral dimensions so as to sealingly engage the walls of a uniformly dimensioned annular chamber through the 360 of rotation and regardless of whether at the longest dimension of the chamber or the shortest dimen sion. As illustrated. the uniformly shaped members are uniformly cylindrically shaped, since this is the easiest form to employ and constitutes the preferred embodiment. The uniform cylindrically shaped members 5! that are illustrated extend to near the connection with the respective aligned piston at the plane 49 at the center of the vee angle a. As illustrated, the cylindrically shaped members 51 extend to the plane 49such that they can be rotated without creating problems with the sealing engagement with the respective inner and outer walls 55 and 57. Also as illustrated, both the cylindrically shaped members 51 and 51A are uniform cylindcrs and extend to the central plane 49. The uniformly cylindrically shaped members 5] and 51A may constitute an integral member that is preformed to the desired \ce angle a. As illustrated, the cylindrically shaped members 51 and 51A are fixedly joined togcther by suitable interiorly disposed brackets and recessed set screws (not shown). The interiorly disposed brackets and the recessed set screws allow retention of the sealing engagement of the respective members 51 and 51A with the inner and outer walls 55 and 57 regardless of the angle of disposition and throughout the 360 of rotation of the respective cylinder blocks 21. Preferably, the respective cylindrically shaped members 51 and 51A have a polished exterior to facilitate sealing with the respective walls 55 and 57.

The radially inner and outer walls 55 and 57 are concentrically disposed about the respective central longitudinal axes of the respective cylinder blocks 21 so as to define, in conjunction with end sealing means, an annular chamber 53 between the central plane 49 and at least one of the cylinder blocks. Preferably, thc respective radially inner and outer walls 55 and 57 extend, as illustrated, between both cylinder blocks and define two respective annular chambers that are continuous and, in effect, define a single chamber. This avoids the problem of having to provide a seal at the central plane 49 and doubles the capacity of the center section compressor 47 without adding signigicantly to the cost.

End sealing means; such as cylinder block end 87 with its sealing lips 89, 90 and annular shoulders 91, 92; define the ends of the annular chamber 53 and sealingly engage the cylindrical members 51.

The respective inner and outer walls 55 and 57 are preferably smooth and are disposed contiguous the exterior walls of the respective members 51 so as to define a fluid tight relationship, or sealing engagement, therewith. The degree of sealing relationship may vary depending upon the application. For example, in some applications, it will be desirable to provide extremely close tolerances such that there is very little fluid flow past respective members 51. in other applications, relatively greater tolerances can be employed if the center section compressor is to be employed as only a blower with relatively low differential pressures across the respective members 51. As illustrated, the respective inner and outer walls 55 and 57 have resilient members, such as rubber coatings 63 and 65, adhered thereto. Specifically, the inner rubber coating 63 is adhered to the exterior of the stationary center support 30 while the rubber coating 65 is adhered to the interior walls of the stationary outer housing 15. Any of the resilient sealing materials that have sufficient resistance to wear can be employed. For example, the polyfluorocarbons, the synthetic rubbers, materials like Ncolite, and thermoplastic materials, including the moreexpensive materials like nylon and Orlon, can be employed as the sealing coatings. In fact, with low friction metals, such as the copper-based metals, on one or both of the surfaces, particularly where the copper-based metals are impregnated with synthetic lubricants, such as silicones or the t'luorinated hydrocarbons, the layers of coating are not necessary. Where the annular chamber is to be employed in conjunction with a combustible mixture, such as in the vee engine 11,, it is imperative that any linings that are employed be resistant to the fuel, such as gasoline. Where a combustible mixture is employed, the inner surface, or liners, must resist the tendency to create hot spots that could cause prcignition dangers and dangers of an explosion. On the other hand. the permanently lubricated surfaces, like brass impregnated with siliconcs or polyfiuorocarhons.

also resist sparking, or the creation of hot spots and are satisfactory.

As will be apparent from a synthesis of FIGS. 1 and 2, the annular chamber 53 that is concentrically disposed about the longitudinal axis of its respective block varies in length from a first location BDC having the greatest, or longest, longitudinal dimension to a second location TDC having the smallest, or shortest, longitudinal dimension. The first location BDC is equivalent to the bottom dead center position in a convention piston device, since the annular chamber intermediate the respective members 51 has its greatest volumetric capacity at this point. The second location TDC is equiva lent to the top dead center position of a conventional piston device, since the annular chamber intermediate the adjacent members 51 has its minimum volumetric capacity at this position. A gaseous fluid trapped between adjacent members 51 in the annular chamber intermediate the radially inner and outer walls 55 and 57 will be compressed in moving from the first location BDC through to the second location TDC. Conversely, as a pair of adjacent members 51 move from the second location TDC to the first location BDC, the chamber volume therebetween expands and is available to take in a fluid, equivalent to a suction stroke of a conventional piston device, when connected with the intake port 59.

The center section intake port 59 is provided for taking in the gaseous fluid. It is connected with the annular chamber 53 upstream of and near the first location BDC for intake of the gaseous fluid. As illustrated, the center section intake port 59 includes a peripherally extending passageway 67 to facilitate influx of the com pressible fluid, such as combustible mixture from the carburetor 31, throughout substantially the entire suction sector of rotation from near the second location TDC to near the first location BDC as the members 51 rotate counterclockwise in FIG. 2. As indicated hereinbefore. the center section intake port 59 is also connected with the carburetor 31. Specifically, the center section intake port 59 is connected with the carburetor 31 via the schematically illustrated intake manifold 69. Thus, the combustible mixture is taken into the annular chamber intermediate the members 51 prior to being compressed during the opposite cycle and discharged via the discharge port 61.

The center section discharge port 61 is provided for discharging the gaseous fluid taken in through the intake port 59 and compressed in the center section compressor 47. The center section discharge port 61 is in fluid communication with the annular chamber 53. As illustrated, the center section discharge port 61 is also connected with the inlet ports 27 by via the central intake passageway 29, FIGS. 1 and 2. The passageway defining the center section intake port 61 is cut away in FIG. 1, although the entry into the central intake passageway 29 is illustrated in part, as shown by curved arrows 78. Similarly, the curved arrows 79 and 81 illustrate the spacial travelof the combustible mixture in flowing through the respective intake ports 27 and into the respective cylinder 81. Thus, when each piston moves to its predetermined first position to open the intake port 27. the compressed combustible mixture flows into the respective cylinder 23 prior to the compression cycle and subsequent ignition by spark plug 37.

In operation, the cylinder blocks, cylinder heads and pistons 21, 22 and 25 of the vee engine 11 are rotated by conventional starter apparatus engaging the respective gears on the shafts 35. As a respective piston and its combustible mixture charge moves past near the top dead center position, the spark plug 37 is fired, the compressed combustible mixture is ignited, and the combustion front begins to move outwardly through the compressed combustible mixture, as illustrated in chamber 71, FIG. 1. The power developed at this point then acts on the face of the respective piston and on the respective cylinder head to force the piston and cylinder head apart, in turn causing automatic rotation of the cylinder heads and blocks such that rotation by the starter is no longer necessary. Air is sucked inwardly through the carburetor 31 where it is admixed with the fuel, such as gasoline, in a conventional carburetion step. The resulting combustible mixture is then sucked inwardly through the center section intake port 59 into the annular chamber 53 between adjacent members 51. As the combustible mixture intermediate the respective members is moved past the first location BDC, it begins to be compressed, reaching its maximum compression before being discharged via the discharge passageway 61 into the central intake passageway 29. The compressed combustible mixture then flows to a respective open inlet port 27 and into its respective cylinder prior to the compression stroke of that respective piston. Conversely, as the piston that has just fired is moved downwardly with respect to its exhaust, or discharge ports 33, the combustion products flow out the exhaust ports 33 and, thence, out the exhaust system as in a conventional two-cycle internal combustion engine. As the piston that has just allowed exhaust of the combustion products moves further downwardly, it opens its respective inlet port 27 for an influx, under a higher pressure than exists in the cylinder, of the combustible mixture from the central intake passageway 29. Thereafter, the combustible mixture that flows into the cylinder is compressed as the cylinder block rotates and the piston simultaneously reciprocates within its cylinder in the rotating cylinder block 21. As the compressed charge reaches the firing position, its respective spark plug causes ignition since it passes the ignition harness to complete the cycle. Thus, automatic supercharging of the internal combustion engine 11 is effected with no moving parts other than those which are required in the engine anyway.

The cylinder members 51 are cooled by the injection of oil via passageway 73 to maintain friction and by a passage of a cooling fluid, such as air, past fins 75.

The respective cylinder blocks 23 are supported on the stationary center support 30 and the stationary outer housing 15 by way of suitable bearings 76.

The uniformly shaped members may take other shapes than the uniform cylinders, as long as they can be rotated through the annular chamber 53. For exam' ple, they may have the shape of an arcuate trapezoid in cross section, where the arcuatcncss is the same as that of the annular chamber. This structure requires that the outer arcuate trapezoidally shaped structure be rotatable with respect to a member that is connected with the piston and keeps its same relative top-ontop position. Thus, such other structures are disadvantageous in requiring moving parts.

This invention is useful over a wide range of applications, as indicated hereinbefore. In the illustrated embodiment it acts as a supercharger (with no additional moving parts) to supereharge an internal combustion engine and has proven very successful. Specifically, it has served a major role in reducing specific fuel consumption for the vee engine 11 below that considered the absolute minimum for internal combustion engines by theoretical automotive engineers. Moreover, it has enabled developing a lightweight engine having a torque at rotational speeds as low as 535 rpm (revolutions per minute) that is greater than large truck engines of more than twice the volumetric capacity and weight running at 2,000 rpm.

In addition, however, the center section compressor 47 may be employed as a first stage of compression when the angle piston device 11 is employed as a compressor or blower. In the illustrated embodiments the center section compressor 47 has been illustrated as a supercharger supplying compressed combustible mixture. If desired, it may be employed as a cooling air pump for supplying air at elevated pressure for cooling air to flow past the fins 45 and 75; alone or in combination with supplying air through a carburetor into an intake manifold.

From the foregoing. it can be seen that this invention achieves the objects delineated hereinbefore and provides one or all of the features delineated as being desirable and not heretofore provided by the prior art apparatus.

Although this invention has been described with a certain degree of particularity, it is understood that the present disclosure has been made only by way of example and that numerous changes in the details of construction and the combination and arrangement of parts may be resorted to without departing from the spirit and the scope of this invention.

What is claimed is:

1. In a rotary device of the so-called angle piston type effecting compression of a gaseous fluid and having:

a. first and second cylinder blocks rotatable about respective central longitudinal axes; said first and second cylinder blocks each having a plurality of radially spaced, substantially parallel cylinders arranged for rotation about respective said central longitudinal axes; the open ends of the respective sets of cylinders being disposed each other, aligned, and disposed at an angle with respect to each other so as to form a vee angle of at least 90 and less than 180;

b. first and second sets of pistons disposed in respective said cylinders, a pair of aligned pistons in aligned said cylinders being connected together at said vee angle a; each said respective pair of connected pistons being rotatable and, by angular displacement, reciprocally movable within and with respect to respective cylinders as said pistons are rotated in a generally elliptical path; said pair of connected pistons maintaining their same relative position of top-on-top as they rotate with their respective cylinders;

. first and second cylinder heads connected, respectively, with said first and second cylinder blocks and rotatable therewith;

d. a plurality of respective inlet ports for intake of a gaseous fluid within respectivecylinders atop respective said pistons therewithin at least by the time said piston and cylinder have attained a predetermined first position; said intake ports being connected with and communicating with said cylinders at said first position;

. a plurality of respective discharge ports for discharging said gaseous fluid of d. from within said cylinder after compression therewithin and at a predetermined second position of respective said pistons and cylinders; said discharge ports being connected with and communicating with said cylinders at said second position; and

1". power delivery means connected with said first and second cylinder blocks for delivery of power with respect thereto;

the improvement comprising a center section compressor that includes:

g. a plurality of uniformly shaped members connected with respective pistons in at least one said set of pistons in at least one said block and extending to near the connection with respective aligned pistons at said vee angle a;

h. radially inner and outer walls and end sealing means defining an annular chamber concentrically disposed about said central longitudinal axis of said at least one block; said annular chamber varying in length from its greatest longitudinal dimension at a first location, equivalent to bottom dead center position, to its smallest longitudinal dimension at a second location, equivalent to a top dead center position; said inner and outer walls being disposed immediately adjacent said uniformly shaped members so as to constrain said members to traverse through said annular chamber and in fluid tight relationship therewith so as to effect compression of a fluid between adjacent said members as they move from said first location to said second location and to effect suction of said fluid into said an nular chamber as they move from said second location to said first location;

i. center section intake port for taking in a gaseous fluid; said center section intake port being in fluid communication with said annular chamber upstream of said first location;

j. center section discharge port for discharging said gaseous fluid of (i); said center section discharge port being in fluid communication with said annular chamber adjacent said second location;

whereby said gaseous fluid can be taken into said annular chamber of said center section compressor imtermediate said members and be compressed as said members having said fluid trapped thercbctween move from said first location to said second location.

2. The rotary device of claim 1 wherein said uniformly shaped members are uniformly cylindrically shaped.

3. The rotary device of claim 1 wherein both said first and second said sets of pistons have said uniformly cylindrically shaped members; two sets of radially inner and outer walls defining two respective annular chambers are concentrically disposed about respective central longitudinal axes of respective said cylinder blocks; said two annular chambers define a continuous chambcr intermediate said cylinder blocks; said respective inner and outer walls are disposed immediately adjacent respective said cylindrically shaped members so as to constrain said members to traverse through said annular chamber and in fluid tight relationship therewith so as to allow compression of a fluid between adjacent said members as they move from said first location to said second location; each annular chamber varying in longitudinal length from said first location to said second location; said center section intake port and said center section discharge port communicate. respectively, with said continuous chamber upstream of said first location and adjacent said second location; whereby said center section compressor has approximately double the compressor capacity of only a single annular chamber type compressor.

4. The rotary device of claim 1 wherein said uniformly shaped members are uniformly cylindrically shaped; both said first and second said sets of pistons have said uniformly cylindrically shaped members; two sets of radially inner and outer walls defining two respective annular chambers are concentrically disposed about respective central longitudinal axes of respective said cylinder blocks; said two annular chambers define a continuous chamber intermediate said cylinder blocks; said respective inner and outer walls are disposed immediately adjacent respective said cylindrically shaped members so as to constrain said members to traverse through said annular chamber and in fluid tight relationship therewith so as to allow compression of a fluid between adjacent said members as they move from said first location to said second location; each section discharge port is connected with said inlet ports I at least at said predtcrmined first position and said gaseous fluid that is compressed in said center section compressor is also compressed within said cylinders.

6. The rotary device of claim 5 wherein said gaseous fluid is an oxygen-containing fluid; said oxygencontaining fluid is admixed with a fuel to form a combustible mixture; said device is an internal combustion engine having ignition means for igniting said combustible mixture in respective said cylinders at a predetermined position; said combustible mixture is burned internally to develop power in said internal combustion engine; and said power delivery means delivers power from said internal combustion engine. 

1. In a rotary device of the so-called angle piston type effecting compression of a gaseous fluid and having: a. first and second cylinder blocks rotatable about respective central longitudinal axes; said first and second cylinder blocks each having a plurality of radially spaced, substantially parallel cylinders arranged for rotation about respective said central longitudinal axes; the open ends of the respective sets of cylinders being disposed each other, aligned, and disposed at an angle with respect to each other so as to form a vee angle Alpha of at least 90* and less than 180*; ; b. first and second sets of pistons disposed in respective said cylinders, a pair of aligned pistons in aligned said cylinders being connected together at said vee angle Alpha ; each said respective pair of connected pistons being rotatable and, by angular displacement, reciprocally movable within and with respect to respective cylinders as said pistons are rotated in a generally elliptical path; said pair of connected pistons maintaining their same relative position of top-on-top as they rotate with their respective cylinders; c. first and second cylinder heads connected, respectively, with said first and second cylinder blocks and rotatable therewith; d. a plurality of respective inlet ports for intake of a gaseous fluid within respective cylinders atop respective said pistons therewithin at least by the time said piston and cylinder have attained a predetermined first position; said intake ports being connected with and communicating with said cylinders at said first position; e. a plurality of respective discharge ports for discharging said gaseous fluid of d. from within said cylinder after compression therewithin and at a predetermined second position of respective said pistons and cylinders; said discharge ports being connected with and communicating with said cylinders at said second position; and f. power delivery means connected with said first and second cylinder blocks for delivery of power with respect thereto; the improvement comprising a center section compressor that includes: g. a plurality of uniformly shaped members connected with respective pistons in at least one said set of pistons in at least one said block and extending to near the connection with respective aligned pistons at said vee angle Alpha ; h. radially inner and outer walls and end sealing means defining an annular chamber concentrically disposed about said central longitudinal axis of said at least one block; said annular chamber varying in length from its greatest longitudinal dimension at a first location, equivalent to bottom dead center position, to its smallest longitudinal dimension at a second location, equivalent to a top dead center position; said inner and outer walls being disposed immediately adjacent said uniformly shaped members so as to constrain said members to traverse through said annular chamber and in fluid tight relationship therewith so as to effect compression of a fluid between adjacent said members as they move from said first location to said second location and to effect suction of said fluid into said annular chamber as they move from said second location to said first location; i. center section intake port for taking in a gaseous fluid; said center section intake port being in fluid communication with said annular chamber upstream of said first location; j. center section discharge port for discharging said gaseous fluid of (i); said center section discharge port being in fluid communication with said annular chamber adjacent said second location; whereby said gaseous fluid can be taken into said annular chamber of said center section compressor imtermediate said members and be compressed as said members having said fluid trapped therebetween move from said first location to said second location.
 2. The rotary Device of claim 1 wherein said uniformly shaped members are uniformly cylindrically shaped.
 3. The rotary device of claim 1 wherein both said first and second said sets of pistons have said uniformly cylindrically shaped members; two sets of radially inner and outer walls defining two respective annular chambers are concentrically disposed about respective central longitudinal axes of respective said cylinder blocks; said two annular chambers define a continuous chamber intermediate said cylinder blocks; said respective inner and outer walls are disposed immediately adjacent respective said cylindrically shaped members so as to constrain said members to traverse through said annular chamber and in fluid tight relationship therewith so as to allow compression of a fluid between adjacent said members as they move from said first location to said second location; each annular chamber varying in longitudinal length from said first location to said second location; said center section intake port and said center section discharge port communicate, respectively, with said continuous chamber upstream of said first location and adjacent said second location; whereby said center section compressor has approximately double the compressor capacity of only a single annular chamber type compressor.
 4. The rotary device of claim 1 wherein said uniformly shaped members are uniformly cylindrically shaped; both said first and second said sets of pistons have said uniformly cylindrically shaped members; two sets of radially inner and outer walls defining two respective annular chambers are concentrically disposed about respective central longitudinal axes of respective said cylinder blocks; said two annular chambers define a continuous chamber intermediate said cylinder blocks; said respective inner and outer walls are disposed immediately adjacent respective said cylindrically shaped members so as to constrain said members to traverse through said annular chamber and in fluid tight relationship therewith so as to allow compression of a fluid between adjacent said members as they move from said first location to said second location; each annular chamber varying in longitudinal length from said first location to said second location; said center section intake port and said center section discharge port communicate, respectively, with said continuous chamber upstream of said first location and adjacent said second location; whereby said center section compressor has approximately double the compression capacity of only a single annular chamber.
 5. The rotary device of claim 4 wherein said center section discharge port is connected with said inlet ports at least at said predtermined first position and said gaseous fluid that is compressed in said center section compressor is also compressed within said cylinders.
 6. The rotary device of claim 5 wherein said gaseous fluid is an oxygen-containing fluid; said oxygen-containing fluid is admixed with a fuel to form a combustible mixture; said device is an internal combustion engine having ignition means for igniting said combustible mixture in respective said cylinders at a predetermined position; said combustible mixture is burned internally to develop power in said internal combustion engine; and said power delivery means delivers power from said internal combustion engine. 